Hydraulic pump or motor



3 Sheets-Sheet l E. K. BENEDEK HYDRAULIC PUMP OR MOTOR Filed Oct. 9,1935 u rru Sept. 19, 1939.

5 2 2 m 3 Q 09 7 2 a I a 3 4 3 I 2 F: E; l-

Sept. 19, 1939.

E, K. BENEDE-K 2,173,432

HYDRAULIC PUMP OR MOTOR Filed Oct, 9, 1935 3 Sheets-Sheet 2 ELEKKJEENEDEK Sept. 19, 1939. 'E K. BENEDEK I HYDRAULIC PUMP OH MOTOR FiledOct. 9. 1935 5 Sheets-Sheet 3 ELEKKLE ENED EK Patented Sept. 19, 1939UNITED STATES PATENT OFFICE 2,173,432 nrnmiumc PUMP on. MOTOR Elek K,Benedek, Bucyrus, Ohio Application October 9, 1935, Serial No. 44,225 11Claims. (Cl. 1o'3 -1c1 This invention relates to'variable displacement,reversible, positive delivery pumps and motors and particularly for usein connection with high pressure fluid power transmission systems. The

5- present pump or-motor is of the general type comprising a rotarycylinder barrel and a surrounding rotary piston actuating reactancewhich are interconnected for synchronous rotation about their respectiveparallel axes through the medium of rigid torque transmitting T-headpistons mounted in cylinders of the barrel and connected to the rotaryreactance.

One of the principal objects of the present invention is to provide apump or motor of this character wherein driving power from a suitableprime mover is applied to the piston actuating rotary reactance insteadof to the cylinder barrel so that the pistons are relieved fromtransmitting the'torques of the rotary reactance and the largeanti-friction bearings thereof.

A correlative and more specific object is to support the barrelrotatably solely upon a stationary valve pintle instead of directly inthe casing; to provide, for cooperation with the bistons of the barrel,an adjustable rotary reactance mounted in the casing and positively andaccurately guided sothat its axis is at all times coincident with orparallel to the pintle axis and in a fixed plane through ,the pintleaxis; and to fixedly support the pintle in the casing in a nonrotativeposition in which the plane defined by the axis of the ,pintle and thedead center line of the pintle valve bridges is at all times coincidentwith the said fixed plane through the pintle axis.

' An equally important object is to provide a structural relation inwhich,-in the dead center positions of each-piston, its'axis coincideswith' 45 Another object is to provide a' pump wherein are combined adirectly driven adjustable reactance rotor, a driving means for therotor supported independently of the rotor and cylinder barrel, and astationary pintle accurately and 50 fixedly mounted for proper timing,tapered for,

uniform stress and for providing accurate adjustment of radial clearancebetween the pintle and barrel, and constrained to absolute rigid coaxialrelation in the barrel. 56 -Another object is to provide a .valvepintle,

barrel, and rotary reactance combination of this character, in which thereactance rotor may be positively driven by an impeller while in anyadjusted position and in which the barrel and pistons are relieved fromall torque except that 5 necessary for-rotating the barrel itself.

Another specific object is to provide for rotating the reactance rotorby an impeller shaft in any-of its adjusted positions, through themedium of a planetating coupling means. 10

Other objects are to provide a more compact and efficient pistonactuating means, and a barrel mounting by which accurate and positivehydraulicclearance between the pintle and barrel may be obtained andwear may be compensated 15 by adjusting the barrel on the pintle.

Other objects and advantages will become apparent from the followingspecification wherein reference is made to the drawings in which Fig. 1is a longitudinal, horizontal axial sec- 20 tional view of. a pump ormotor embodying the principles of the present invention, and is taken ona plane indicated by the line l--l in Fig. 2;

Fig. 2 is a vertical cross sectional view taken on the plane indicatedby the line 2-2 in Fig. 1; 25

Fig. 3 is a fragmentary side elevation of a piston illustrating a pistonreactance block and an anti-friction roller bearing assembly showing thecylindrical load transmitting shoulders of the Fig. 4 is a end elevationof the driving element of the impeller means for driving one end of theplanetating coupling disc;

Fig. 5 is a front elevation, partlyin section, of the element.illustrated in Fig. 4; 35

Figs. 6, 7 and 8 are, respectively, a left end elevation,a frontelevation, and a right'end elevation of the planetating disc member ofthe planetating coupling mechanism;

Fig. 9 is a fragmentary sectional view of the 40 reactance rotor;

Fig. 10 is a right end elevation of a portion of the reactance rotorillustrated in Fig. 9, Figs. 9 and 10 showing the means on the reactancero-.

tor for connecting the planetating disc and the reactance rotor at oneend of the disc.

Referring to the drawings, the working parts of the structure aremounted in a liquid tight casing l which is in the form of an annularbody portion open at one end and having at the opposite end an integralradial wall portion 2, the wall portion terminating in a rigid hubportion 3 which forms the valve head of the pump. The open end of thebody I is closed by a suitable end cover 4 secured to the end of thebody I by suitable bolts 5 and forming therewith a substantiallyrigidunitary closed housing structure. Mounted in the hub 3 of the body is ashank portion 6a of a pintle 6 which pintle extends into and in coaxialrelation with the body I and has a tapered valve portion 6b.

In the valve portion 617 of the pintle are diametrically oppositereversible valve ports I and 8 respectively, separated from each otherby circumferentially extending bridges 9 and I0, one of the ports beinga fluid pressure port and the other a suction port concurrently. Theport I is in communication with longitudinal ducts II in the pintle andthe port 8 is in communication with longitudinal ducts I2. The ducts II,in turn, communicate with a main port I3 in the shank 6a of. the pintleand the ducts I2 communicate with the other main port I4 in the shank ofthe pintle, The main ports l3 and I4 are diametrically opposite withrespect to each other and are connected respectively through suitableducts formed in the hub portion 3 of the casing with a pressure conduitand a suction, conduit, in a well known manner, the pressure conduitleading to a suitable hydraulic machine to be operated and the suctionconduit leading to a suitable sump or to the exhaust of the machine. Onthe pintle 6, at the ends of the tapered valve portion 6b, arecylindrical bearing surfaces 6c and 611, respectively, on which aresupported the inner races I1 and I8 respectively of tapered radial loadand axial thrust bearings I9 and 20, having outer races 2| and 22respectively. The valve portion 61) of the pintle is tapered from theportion 60 to the portion 6d at a very pronounced taperso that thepintle approximates as nearly as may be a constant strengthend-supported beam whereby substantially uniform stress results thereonand deflection of the pintle is eliminated even in the absence of endsupport at the free end because of the extra strength at the mounted orshank portion.

Mounted on the pintle is a cylinder barrel 24 having at each end aninternal axially extending annular shoulder and an intersectingradialshoulder, which shoulders receive and fixedly accommodate outer races 2l and 22 respectively of the bearings I9 and 20, for supporting thebarrel in coaxial relation to the pintle. The barrel is provided with avalving bore which is tapered complementary to the valve portion 6b .ofthe pintle and which, when the barrel is mounted on the bearings I9 and20, receives and fits the tapered valve portion 61) of the pintle. Aslight but very positive adjustable clearance is provided between thewall of the barrel bore and the complementary tapered valve portion 612of the pintle, the roller elements I9 and 20 having suflicient capacityto maintain this clearance under all pressure conditions so that an oilfilm may be formed between the pintle and barrel bore wall for effectinga seal between the barrel and pintle, for preventing seizure andheating, and hydraulically balancing the pintle to eliminate unbalancedhydraulic load.

Due to this high capacity dual bearing mounting of the barrel directlyon the fixed and rigid pintle instead of in the housing of the pump, anaccurately determined mounting of the barrel in relation to the pintleis provided in which concentricity of the pintle and barrel, with properpositive clearance between the pintle and barrel is absolutely assured.This mounting, therefore,-

whereby the proper radial and axial relations of the pintle and barrelare maintained may be referred to as a positive mounting. Among itsadvantages are the facts that eccentricity of the pintle and barrel andinaccuracies in radial clearance, due to separately pressing the pintlein the casing and separately supporting the barrel in the casing, areentirely eliminated. Consequently, the pintle cannot seize in the barreldue to inaccuracy in alignment with the barrel or to eccentricity of thepintle and barrel.

To provide for axial adjustment of the barrel on the pintle, in case itbecomes necessary due to wear of the bearings I9 and 20, or for otherreasons, the outer or free end portion lie of the pintle is threaded andreceives an adjusting nut 25, which engages the end of the inner bearingrace I8 so that by operation of the nut 25, the race I8 can be adjustedaxially toward the valve portion 6b, and through the medium of thetapered bearing elements and races can positively move the barrelaxially toward the shank of the pintle for decreasing the radialclearance between the bore wall and portion 6b of the pintle. Veryslight movement of the barrel in this manner will positively adjust andmaintain the radial clearance between the pintle and barrel bore afterwhich an outer lock nut 26 may be tightened for retaining theadjustment. In order to permit such adjustment, slight clearance, notshown, axially of the rotary reactance is provided between the lateralfaces of the piston T-head and guide ways of the rotary reactance, aswill later be described.

The race I! is stationary with respect to the pintle while the race I8is movable axially thereon. Thus for adjustment for wear the bearingassembly including the bearings 20, the race I8, and the race or cone 22may be shifted bodily axially and, when so shifted, effects acorresponding axial shifting of the barrel, which necessarily carrieswith it the race or cone 2| of the bearings I9. Since the race I1 isfixed with respect to the pintle, this movement causes tightening of thebearings I9 to eliminate radial clearance in the bearing itself. At thesame time, this movement permits a reduction in radial clearance betweenthe barrel bore andthe tapered portion of the pintle. If the wear on thebearings I9 is so great that movement of the barrel axially theretowardto effect the proper reduction of radial clearance of the bearings I9reduces too greatly the radial clearance between the pintle and barrel,the bearings I9 must be replaced or shims must be placed between therace I! and the cooperating radial abutment shoulder of the pintle.

For effecting the adjustment, the adjusting nut 25 is tightened untilthe barrel is difficult to rotate. The nut 25 is then backed away on thescrew portion lie of the pintle a definite fraction of one revolution,the amount of turning of the nut 25 depending upon the taper per inch ofthe barrel bore and pintle portion 6b and the pitch of the threads onthe portion 66 of the pintle. For example, if the taper is one eighth ofan inch per each inch of length of the pintle, and a total radi'alclearance of .001 inch is required, this can be obtained by adjustingthe barrel .008 inch axially. Knowing, the pitch of the particularthreads on the pintle portion 63, the amount of rotation of the nut 25to effect an exact amount of clearance between the barrel bore andtapered portion of the pintle is readily determined.

For permitting the axial adjustment of the race I8, a small clearancerecess 20a is provided between the portions 6b and 5d of the pintle,this recess being coextensive axially oi the pintle with the normalclearance space between the race l3 and the corresponding end of thebarrel. It should be noted, however, that due to the taper of the pintleand the positive radial clearance between it and the barrel, thehydrostatic pressure urges the barrel toward the bearings 20 so that thebearings 20 are subjected to appreciable thrust and resultant wear,whereas the bearings I! are subjected to substantially no axial thrust.Furthermore, since the tapered portion of the" pintle is axially short,the pressure film is coextensive axially therewith, and substantially nowear occurs on the pintle portion 1), the bearlngs I 9, or bearings 20due to unbalanced load. Consequently, misadjustment of the barrel on thepintle results primarily from wear of the bearings 23 and resultanttravel of the barrel toward that end of the pintle. The adjustment above.described, therefore is eflective for maintaining the properclearances.

Thus with the barrel mounted on the pintle 'as described, instead of inthe casing, arcuate clearance and relationship between the pintle andbarrel is maintained at all times and the barrel and pintle form asubstantially self-contained unit. Since the valve portion is very shortand the taper very pronounced, and the radial clearance is positivelymaintained, an eflective oil film is maintained between the barrel andpintle coextensive with the valve. portion 6b. Substantially hydrostaticbalance of the barrel and pintle results and the only torque necessaryfor rotating the barrel is that to overcome the slight and negligiblefrictional resistance of the barrel itself Y and viscuous friction ofthe fluid.

The barrel is provided, in the zone of the pintle valve portion 617,witha plurality-of circumferantially spaced radial cylinders 21, each ofwhich has a cylinder port 28 cooperable successively with the ports Iand 3 of the pintle as the barrel rotates. Mounted one in each cylinderare radial pistons 23,'each of which has a rigid T-head 30, later to bedescribed, for eifecting load transmission between the pintle and rotaryreactance, and torque transmission between the rotary reactance andbarrel. I

The rotary reactance comprises a generally annular member 32 surroundingthe barrel and having a cooperating annular ring 33 which forms thecircumferentially closed wall of the member 32, the member 32 and ring33 thus providing a series of generally chordal recesses in which arereceived, respectively, the T-heads 33 )1 the pistons. The members 32has a series of openings 32a for accommodating the pistons and hasshoulders 32b engaging the radially inward faces of the piston T-headsfor actuating the pistons on the radially outward strokes.

Mounted within the recesses are reactance clocks or interponents 34,each of which has an inwardly disposed chordal face and an outwardlydisposed cylindrical face, the cylindrical l of the blocks 3 isprovided, at its inner face, with a trough 34a in which arereceived aplurality of elongated hydralically caged rollers 35, ,the rollers beingeither true capillary cageless needle rollers or larger rollers but, inany event, so spaced that the total clearance therebetween in thedirections of rolling movement is such that only. capillary spacing ofeach roller from the others and from the ends of the trough 34a ispermitted. By this arrangement, slip fluid may enter the trough 34a andthe centrifugal pressure fluid will maintain the proper pressure andcapillary oil films between the T-heads and the blocks 34' and capillaryfilms between the rollers 35, so that combination, high pressure, oiland capillary and anti-friction bearings are provided.

24b, both the inner and outer surfaces of the shoulders beingcylindrical and coaxial with each' other about an axis parallel to orcoincident with the axis of ;the reactance rotor or barrel.'Complementary cylindrical shoulders are formed on the radial walls ofthe member 32, as indicated at 32c, and'engagethe inner cylindricalwalls of the shoulders 34b. The outer .walls of the shoulders 34b engageand are complementary to the inner cylindrical wall surface of the rings33. 1 Consequently, on the suction strokes of the pistons, the clearancebetween each T-head and its associated block 34 will be coextensive withthe T-head and positively formed for admitting slip fluid therebetween.

As hereinbefore mentioned, clearance axially of the reactance rotor isprovided between the lateral faces of the T-heads 33 and alignedradialwall portions of the recesses so that, upon axial ;adjustment ofthe barrel, the T-heads may ac- 'As better illustrated in Figs. 1 and 3,eachofv the blocks 34 has laterally extending shoulders surface of thering 33, so that they may shift circumferentiaily of the. reactancerotor for selfalignment in operating position and for creating oilfilms-on all of their surfaces.

' The reactance rotor is mounted through the medium of heavyanti-friction bearings 36 in and coaxial with an adjustable reactancestator 31, the reactance stator and reactance rotor being constrained tocoaxial relation with respect to each other at all times, The stator 37,in turn, is provided at its outer surface with diametrically oppositeflat slide bearing surfaces 38 which cooperate with complementarysurfaces 39 formed on the interior of the casing I so that the stator 31may be adjusted in either direction from coaxial relation with thepintle to an eccentric relation therewith. lit is important to note,however, that at all times the reactance stator, and consequently thereactance rotor, maintains a position in which its axis of rotation iseither coincident with or parallel to the-pintle axis and lies at alltimes in a fixed plane deflned by the dead centerline of the bridges 9and ID of the pintle and the axis of the pintle. "Thus the reactancerotor moves, during adjustment, with its axis always in a plane throughthe axis of the pintle and the dead center of the bridges whileremaining parallel to the pintle axis. Consequently in any adjustedposition of the reactance rotor, the pistons are at their extremeoutward or inward position in the cylinders when aligned with andcentered on the dead centers of the respective bridges. For adjustingthe reactance housing and rotor fronrthe outside of the casing, suitablecontrol rods are provided.

Heretofore, in pumps and motors in which both 'a driven rotary reactancewas to be utilized, and variable displacement was to be efiected thepractice was to provide a driven means coaxial with the reactance rotorand to effect the variable displacement by shifting the pintle and thebarrel. Two manners of effecting this relative shifting of the barreland pintle are now utilized. The first is to mount the pintle at the endof a pendulum or swinging arm and provide flexible joints or connectionsbetween the-ducts of the pintle and the remainder of the hydrauliccircuit so that the pintle can be swung to different positions duringoperation of the pump. In this type of structure, however, when thepintle is thus swung about a fixed point eccentric to its axis, therenecessarilyoccurs a .partial rotation of the pintle about its own axis.The eccentric disposition of the rotary reactance, on the contrary, isfixed in position circumferentially of the pintle. Therefore, when thepintle is concentric with the rotary reactance, a condition occurringonly at zero stroke, the bridges of the pintle are in a normalcircumferential position relative to the reactance rotor, in which thedead center plane of the bridges and eccentric plane of the barrel andreactance are identical. Upon swingin'g the pintle, however, the bridgesare rotated out of the proper dead center with respect to the plane ofeccentricity so that they are either prevented and undue precompressionand expansion of the pressure fluid results in dynamic unbalance of thepintle with the accompanying disadvantages of extreme hammering, wear,vibration and destruction of the pump structure.

Again the pintle of such structures necessarily must be shiftable foradjusting the stroke in the very plane in which the greatest hydraulicload occurs, that is, in the plane of the dead center positions of thepistons. Necessarily, therefore, the pintle cannot be permanentlysecured against movement in these directions.

Here is should be noted that the pump of the present invention is forextremely high pressures, in which the eccentricity must be accuratelymaintained, and for such use the prior structures would be inoperable.

First, in theswinging pintle pump, when operated at high pressures, thepintle gradually creeps to zero stroke position, the stroke continuouslyvarying until this position is reached. Again, it is impossible tosupport the swinging arm on a pivot and the pintle on the arm at aposition remote from the pivot with sufllcient rigidity to preventdeflection ortipping of the pintle and deflection of the arm itself.These deflections change the relation between the pintle and otheroperating parts of the pump. This disadvantage cannot. be overcome byshortening the supporting arm, as this in turn would result in greaterrotation of the pintle about its own axis for a given eccentric setting.

The present pintle, as explained, is supported fixedly in the casingwith the dead center line of the pintle bridges lying in a fixed planedefined plane.

by the axes'of the pintle and reactance rotor, later to be described, inall adjusted positions of the rotor, so that the dead center position ofthe pistons is always in the same plane as the dead center of thebridges. Thus accurate timing is assured. As a result, properpre-compression and expansion of the working fluid in the cylinders isobtained and smooth, silent operation provided. Were accurate timing notprovided, as is the case with prior structures, undue precompression ofthe fluid and only partial filling of the cylinders would result andcause excessive noise, hammering and vibration. At high pressures, thevibrations due to this mistiming between the pintle and cylinders aretransmitted to the swinging arm, causing periodic oscillation thereofwhich disturbs the relation of the pintle, barrel and reactance andcauses dangerous vibrations throughout the structure.

Another attempt has been made to maintain.

proper valving relation and variable delivery by mounting the pintle forstraight line adjustment between ways extending parallel to the deadcenter plane of the pintle bridges, the reactance rotor having its axisfixed in the said dead center This structure also requires a telescopingor flexible connection between the pintle and external fluid circuit.Aside from this disadvantage, it also fails to maintain the accuracy ofsetting required, due, primarily, to the fact that the slot or supportin which the pintle is mounted for sliding to and fro in a straight linemust necessarily extend parallel to the plane through the axis of thepintle and dead center of the bridges. Thus, at dead center pistonpositions, the directions of greatest forces applied to the pintle,there is no resisting support and the pintle tends to rock in theeccentric plane through the bridges and gradually works towardconcentric position with respect 'to the reactance rotor.

Attempts were made to support the opposite end of the pintle in suitablehearings in the barrel with a corresponding slot. However, when thepintle is disposed eccentrically in the bearing at such end, forcestransversely of the slot are translated into both tangential and radialforce components'which, in turn, tend to twist or subject the pintle totorque.

Thus five conditions must be met concurrently if successful operation isto be obtained, namely: (a) a directly driven rotary reactance is to beutilized; (b) variable displacement is to be provided; (c) accuratetiming'must be maintained; (d) the pintle must be fixedly and rigidlyfixed in position; and (e) adjustment of stroke must be in the plane ofthe dead center line of the bridges and dead center plane of thepistons.

Obviously, theflrst type of prior structure fails to meet, among others,conditions 0, d, and e;

the second, conditions 0 and d, and others various ones of theseconditions. None of the priorthe reactance rotor, the reactance rotorcarries at the and adjacent the free end of the pintle, a hub portionhaving a radial end'wallill, closing the entire end of the rotor. Theend wall II, in turn, has at its outer surface a diametral slot a foreffecting. a driving connection between it and a suitable planetatingdisc, to be described. An

impeller shaft 5| is mounted on suitable setsof tapered bearings 52 inthe end cover 4, the bear- -ings cooperating'to consrain the shaft tofixed axial position. Carried on the inner end of the shaft 5| is a faceplate 5la on which is provided a diametral slot 5lb. For connecting thereactance rotor and shaft 5| through the medium of the slots 50a and5Ib, a planetating interponent or disc 53 is provided. A's betterillustrated in Figs. 6 to 8 inclusive, the disc has at the face adjacentthe reactance rotor a diametral tongue 53a which is slidably received inthe slot 50a, and has at its opposite face a tongue 53!) which isslidably and snugly accommodated in the slot 5") of the plate 5la. Thetongues 53a and 5311 are both diametral and extend at right angles toeach other, and the disc or interponent is snugly received between theend wall 50 of the reactance rotor and the face plate 51a of the shaft5|. Consequently, in any eccentric position of the reactance rotor, onecomponent of eccentricity may be compensated by travel of the tongue 53aalong the slot 50a and the complementary component of eccentricity maybesimultaneously compensated by travel of the tongue 53b along the slotSlb. If desired, suitable antifriction means may be provided foreffecting better anti-friction cooperation between the respectivetongues and slots.

Since the impeller shaft is maintained at all times in concentricrelation to the pintle and in fixed axial position by its independentmounting in the bearings 52, no vibrations or axial thrusts due to thedriving connection are transferred by it to the reactance rotor, allsuch vibrations and forces being taken by the bearings 52, as also areall axial thrusts on the shaft. Therefore, the reactance rotor issubjected only to radial hydraulic load and the actual torqueforcesdeveloped for rotating the barrel. The pistons themselves are relievedfrom any rocking movement and stresses tending to rock them as they needonly transfer to the barrel the negligible torque required to rotate thebarrel itself. All forces and vibrations, therefore, are segregated tothe independent sub-assemblies.

Since the reactance rotor is directly driven by the impeller, the powerrequired to rotate the reactance rotor and itslarge supporting bearings,

is directly applied to the rotor and does not have to be transmitted bythe pistons; as in the case wherein the barrel itself is driven directlyby. an impeller shaft. Instead, the only torque which must betransmitted by the pistons is that necessary for rotating the freebarrel, the relatively small pitch diameter bearings l9 and 20 for whichthe power required is negligible due to the pintle being hydrostaticallybalanced, the bearings generally under no iunbalanced load, and toovercome the viscuous friction between the barrel and pintle. Since inany eccentric position of the rotor, the planetating interponent assumesa' given axis of rotation of its own and is in any event relativelylight in comparison with the power transmitted, substantially nounbalanced forces result therefrom which might cause vibration of any ofthe other parts.

The present structure also lends itself to cooperation with a primemover having its impeller shaft coaxial at all times with and directlyconnected to the reactancerotor, the prime mover being mounted foradjustment concurrently with the reactance rotor to different eccentricpositions.

Another advantage of the present structure is that the adjustment is byadjustment of the rotary reactance and hence in the plane of the pistonsinstead of spaced from the piston plane, as in the case of adjustablepintles.

Again, since the reactance rotor is sealed at one end by the wall 50,slip-fluid may be retained readily on all the working parts by provisionof a shield at the open end of the reactance rotor.

It is apparent from the foregoing description that a simple, compact andhighly efficient variable displacement type of rotary, radial piston,pump or motor is provided in which the rotary reactance is directlydriven so as to relieve the pistons from the torque necessary to rotateheavy, large pitch diameter supporting bearings and at the same time,the disadvantages inherent in the shifting pintle type of structure areeliminated. What appears at first glance to be a reversal of parts, inthat the pintle is stationary and the reactance is shifted, whereas inprior structures the rotary reactance is fixed and the pintle isshifted, is found, upon closer consideration to result in' operationswhich cannotbe produced by the prior structures and in elimination ofdisadvantageous effects inherent in the prior structures.

Having thus described my invention,

I claim:

1. In a rotary, radial pistonpump or motor, a casing, a rotatable barrelhaving a set of radial cylinders, valve means for the cylinders, pistonsin the cylinders respectively, a rotary reactance for actuating thepistons, means supporting the reactance for rotation about its axis andfor adiustment and constraining the reactance to adiusted positionswherein its axis is parallel to and in a fixed plane through the axis ofthe pintle, an impeller rotatably supported independently of the barreland reactance in fixed position radially of the casing and in axialalignment with the pintle, and planetating means operatlvely connectingthe impeller and rotary reactance for effecting driving relationtherebereactance to positions wherein its axis is in a' fixed planethrough the pintle axis, an impeller coaxial with the pintle and mountedin the casing independently of the barrel and in fixed positionradially, planetating means drivingly connecting the impeller andreactance rotor in all adjusted positions of the reactance, and meansfor adjusting the reactance to vary the stroke.

3. In a rotary, radial piston pump or 'motor, a.

:asing, a pintle fixedly mounted therein, a barrel supported on thepintle and constrained to con centricity and positive radial clearancewith respect thereto, and having a plurality of radial cyl-- inders,pistons in the cylinders respectively, said pintle having portsinyalving cooperation with the cylinders, a reactance rotor foractuating the pistons and disposed in surrounding relation to thebarrel,an adjustable stator in surrounding relation to the reactance forsupporting the reactance, bearing means interposed between thereactancev and stator and supporting the reactance for rotation aboutthe reactance axis, means mounting the stator for adjustment todifferent eccentric positions with respect to the pintle wherein theaxis of the reactance is in a fixed plane through the pintle axis, animpeller means mounted independently of the barrel and reactance and infixed position radially in the casing, and planetating means drivinglyconnecting the impeller means to the reactance, for concurrent rotationof the impeller means and reactance about their respective axes.

4. In a rotary, radial piston pump or motor, a casing, a pintle mountedby one end therein, bearing means positively mounting the barrel on thepintle with fixed radial clearance space therebetween, said barrelhaving radial cylinders, pistons in the cylinders respectively, saidpintle having ports in valving cooperation with the cylinders, rotaryreactance means adjustably mounted in the casing in surrounding relationto the barrel for adjustment to different eccentric positions relativethereto and being connected to the pistons for actuating the same, saidreactance means having a transverse disc portion spaced axially of thepintle beyond the free end of the pintle and adjacent the end of thebarrel, an impeller rotatably mounted in fixed radial position in thecasing and having a disc portion spaced axially from and being parallelto the transverse disc portion of the reactance means,

and planetating means interposed between said' disc portions 'of thereactance means and impeller and drivingly connecting the same torelieve the pistons and cylinders from the driving torque necessary torotate said reactance means.

5. In a high pressure, variable displacement, rotary, radial piston pumpor motor, a casing, a rotatable barrel having a plurality of radialcylinders, pistons in the cylinders respectively, a pintle in valvingcooperation with the cylinders and fixed in position in the casing,rotary reactance means for the pistons, impeller means mounted in thecasing in axial alignment with the pintle for driving the reactancemeans, planetating means connecting the reactance means and impellermeans in all adjusted positions of the reactance means, means mountingthe reactance means for adjustment to different positions of eccentricrelation with respect to the barrel while constraining the Zreaotancemeans to adjusted positions wherein its axis is in a fixed plane throughthe axis of the pintle, and control means engaging the reactance meansin the zone of the pistons, and extending radially of the reactancemeans in said fixed plane, whereby working reactance forces are moreefiiciently applied.

6. In a high pressure, variable displacement, rotary, radial piston pumpor motor, a casing, a rotatable barrel having a plurality of radialcylinders, pistons in 'the cylinders respectively, a pintle havingdiametrically opposite ports and bridges therebetween, and being invalving co" operation with the cylinders and fixed in position in thecasing, rotary reactance means for.

the pistons, impeller means mounted in the casing in axial alignmentwith the pintle for driving the reactance means, planetating meansconnecting the reactance means and impeller means in all adjustedpositions of the reactance means, means anti-frictionally mounting thereactance means for rotation and supporting the reactance means foradjustment to difierent positions of eccentric relation with respect tothe barrel while constraining the reactance means to adjusted porotors.

mounted in the casing, a cylinder barrel rotatably supported on thepintle and having a valve bore fitting the valve portion of the pintleand constrained to concentric relation and positive radial clearancewith respect to the pintle valve portion, said barrel having a pluralityof radial cylinders, pistons in the cylinders respectively, said pintlevalve portion having diametrically opposite valve ports for thecylinders and bridges therebetween, a reactance rotor surrounding thebarrel in the plane of the pistons and connected to the pistons foractuating the same, impeller means fixedly mounted in the casing inaxial alignment with the pintle, planetating means connecting thereactance means and impeller means in all adjusted positions of thereactance means, means in the casing and positioned axially of thereactance means in the zone of the pistons for adjustably supporting thereactance rotor for movement to vary the stroke and constraining therotor to positions wherein its axis is parallel to or coincident withthe pintle axis and in a plane defined by the pintle axis and deadcenter line of the pintle bridges.

8. In a rotary, radial piston, variable delivery pump or motor, acasing, a stationary pintle mounted in fixed position therein and havinga valve portion, a, cylinder rotor supported solely by the pintle andhaving radial cylinders in valving cooperation therewith, pistons in thecylinders respectively, positive mounting bearing meansoperatively-interposed between the cylinder rotor and pintle, anadjustable stator, a reactance rotor connected to the pistons foractuating the same, positive mounting bearing means rotatably supportingthe reactance rotor in the stator and entirely independent of thecylinder rotor, an impeller, positive mounting bearing means rotatablysupporting the impeller in the casing independently of the rotors and infixed axial alignment with respect to the pintle, and planetating meansdrivingly connecting the impeller to the adjustable rotor in alladjusted positions of the adjustable rotor.

9. In a variable delivery, rotary, radial piston pump or motor, an innerand an outer rotor, one

of said rotors having radial cylinders, valve means for the cylinders,pistons in the cylinders and connected to the other rotor for operationthereby, means mounting and constraining said rotors to adjustment intopositions wherein their axes are coincident or parallel and in a. fixedplane, said means being positioned in the plane of the cylinders andpiston actuating rotor, and control means operative to move the rotorsrelatively into difierent adjusted positions by force applied radiallyalong the dead center positions of the pistons, and impeller means incoaxial relation with the axis of rotation of the cylinder rotor andplanetating means operatively con-' necting the impeller means and thepiston actuating rotor for driving the piston actuating rotor in allrelatively adjusted positions of,said Y 10. In a rotary, radial piston,

variable delivery 7 a,1vs,4sa pump or motor,'a rigidcaslng, a pintlefixedly secured therein, a cylinder barrel rotatively positively mountedsolely on said pintle and having a plurality of radial cylinders,pistons in the cylinders, said pintie having diametrically oppositevalve ports in valving cooperation with the cylinders and bridgesbetween the ports, a reactance stator positioned axially of the casingin the zone of the cylinders, a reactance rotor'rotatably mounted in thestator, an impeller means, .means' rotatably mounting the impeller meansin the casing and constraining the impeller means "to fixed radialposition in the casing, planetating means operatively interposed betweenthe reactance rotor and impeller means for drivingly connecting the sameat all times, means in the casing in the said zone of the cylinderssupportingithe stator for-adjustmentparallel to a plane 7 I defined bythe pintle' axis and dead center line or the bridges to difierenteccentriccpositions, and

means operating in said zone of the cylinders ror moving the stator tosaid adjusted positions.

' site slidefbearing surfaceson thestator in coop- 11. In arotary radialpiston reversible pump opposite portspvalve bridges between said ports,

an adjustable stator surrounding the pintle at c the.valve portion,guide means in fixed position relative to the pintle and having a pair.of flat or motor, a casinmapintle mounted in the casing and having avalve portion with diametricallywith respect to the pintle anddiametrically opposite trom each other and parallel to the plane definedby the pintle axis and dead center line of the bridges, and positionedin radial alignment with thepintle valve portion, diametricallyoppoeration with saidmflrst bearing surfaces respectively for supportingthe stator for adjustment to parallelrguide surfaces symmetricallyarranged dially'in the casing, planetatingmeans drivingly 1 connectingthe reactance rotor and impeller means in all adjusted positions 01. thereactance rotor, and control means for moving thestator to diilerentadjusted positions tovary the stroke, said control means beingpositioned at the intersection of the plane defined by the pintle axisand dead center line of the bridges with the plane. of

the piston axes, and operative'along said intersection for moving thestator.

' ELEK x. EENEDEK.

